High pressure vane pump



HIGH PRESSURE VANE PUMP 5 Sheets-Sheet 1 Filed June 15, 1962 FIG.

INVENTDR TAK ASl NAMl KAWA @WLMM Arroanevs Feb. 16, 1965 TAKASHINAMIKAWA 3,169,487

HIGH PRESSURE VANE PUMP Filed June 15, 1962 5 Sheets-Sheet 2 F I G 2Iuvem-oa TAKM NANUKAWA E, MWLAMM{ 'KWAM Feb. 16, 1965 TAKASHI NAMlKAWA3,169,487

HIGH PRESSURE VANE PUMP Filed June 15, 1962 5 Sheets-Sheet 3 INVENTORTAKAH NAN KAWA baroauei s Feb. 16, 1965 TAKASHI NAMIKAWA 3,159,487

HIGH PRESSURE VANE PUMP Filed June 15, 1962 5 Sheets-Sheet 4 Imam-cmTAKASI NAMIKAWA AAWummpw m ATTORNE1$ Feb. 16, 1965 TAKASHI NAMIKAWA3,169,487

HIGH PRESSURE VANE PUMP Filed June 15, 1962 5 Sheets-Sheet 5 FIG.I|

FIG l2 FIG I3 INVENTOR AM NAMIKAWA W lira-U I Bmjnn's Atromqs UnitedStates Patent ice 3,169,487 I HIGH PRESSURE VANE PUMP m.TakashiNamikawa, Knre City,"Japan, assignor to Yehan Numata, Yokohama,Japan 7 Filed June 15, 1962, Ser. No. 202,717 Claimspriority,application Japan, Nov. 29, 1961,

1 Claim; (Cl.103 1 29) My invention relates to a high pressure vane pumpcomprisinga valve plate and an intermittently driven rotor. I

and a concentric rotor is intermittently rotated. The cylinder and rotorare provided with overlapping vanes, and these define the end wallsof'ch'arnbers which expand and contract due to the difference betweenthe movements of the cylinder and rotor. During expansion, thesechambersregister with the inlet ports of the valve plate, and during compressionwiththe outlet ports.

The pump thus has over reciprocating pumps the advantage that it may bedirectly drivenfrom a rotating shaft, yet its mechanism is simplerthanthat of centrifugal pumps.

Since some chambers are in the compression stage In this pump the pumpcylinder is continuously rotated while others are expanding there isa-relatively even flow ii of fluid, a decreased pulsation of oilpressure, and excel- Other objects and advantages'of the invention arein part obvious and will in part be set forth in the course of thefollowing description of a preferred embodiment of the invention. Thisembodiment is described in conjunction With the annexed drawings, inwhich:

FIG. 1 is an end view of my new pump;

FIG. 2 is an axial section taken through the entire pump, except for thevalve plate, which is sectioned along the line IIII of FIG. 1;

FIG. 3 is a schematic cross-section through the pump cylinder and rotor;

FIGS. 4, 6, 8, 10 and 12 schematically show various positions assumed bythe vanes relative to the ports;

FIGS. 5, 7, 9, l1 and 13 show the positions of the members of the Genevamovement when the vanes occupy the positions shown in FIGS. 4, 6, 8, 10and 12, respectively;

FIG. 14 is a graph showing the angular positions of the cylinder androtor as a function of time.

Like reference characters denote like parts throughout the severalviews, except that in FIGS. 4, 6, 8, l0 and 12 the characters V1, V2, V3and V4 are used .to identify individual vanes identified as a class bythe reference numeral 7 in FIGS. 13, and reference characters V1, V2, V3and V4 are used to identify individual vanes identified as a class byreference numeral 6 in FIGS. 1-3.

Referring now to FIG. 2, it will be seen that the pump comprises astationary casing 1 closed at one end by the valve plate 2. A cylinder 3is carried by bearings 16 and 20, located in the casing 1 and valveplate 2 respectively. Within this cylinder is mounted the rotor 4,carried by the shaft 5. As best seen in FIG. 3, the inner Wall of thecylinder is provided with inwardly projecting vanes 7, and the rotorcarries peripherally radiating vanes 6. These vanes overlap to form withthe cylinder walls a plurality of expansible chambers. The volume ofthese chambers is varied by rotating the cylinder 3 at a constant speed,while driving the rotor 4 intermittently at an angular speed twice thatof the cylinder.

The,cylinder 3 is biased against the valve plate 2 by the spring 17which is compressed between the bearing 16 and thrust bearing 15.Between the cylinder 3 and casing 1 is an oil reservoir 19. The valveplate 2 is provided with four exhaust ports b and four suction ports 0.As best seen in FIG. 2, each exhaust port b is connected through theoutlet 14 and passage d to a safety valve 8, which is connected throughthe passage e to the inlet 13 and thus to the suction ports 0.

When the delivery pressure exceeds a prescribed limit, the valve member3 is forced open against the resistance of'the spring 9, and oil passesthrough the passage e and suction port c, and thence back into thecylinder 3. The pressure required to open the valve 8 may be adjusted byturning the threaded. plug 33 so as to increase or relieve thecompression of the spring 9.

The valve 10 controls the passage 1 between the oil reservoir 19 and theinlet 13. This valve, which is biased shut by the spring 11,automatically opens when the suction pressure falls too low, and thepressure differential required to actuate it may be regulated by turningthe threaded plug 12. a

The cylinder 3 is formed in two parts to permit insertion of the rotor4, and these two parts are held together by bolts 30. The shaft 5rotates in the cylinder, leakage therefrom being prevented by thesealing rings 31 and 32. One end of the shaft projects beyond thecylinder jinto bearing 28 in journal box 29. Both rotor shaft 5 andcylinder 3 are driven from a drive shaft 25 carried in bearings 26 and27. The cylinder is driven through reduction gearing 21, 22, and therotor shaft 5 through Geneva gearing 23, 24, so that it rotatesintermittently, turning during only half the time that the cylinderturns, but at twice the speed. While Geneva gearing is shown to producethis relationship, it will be appreciated that any other means whichproduces the same efiect may be used. The Geneva gear 24 is keyed to therotor shaft 5 by the key 18.

The operation of the pump will now be explained with reference to FIGS.4-14. FIGS. 4, 6, 8, l0 and 12 show successive positions of the vanesrelative to the valve plate and the apertures therein. FIGS. 5, 7, 9, l1and 13 show the positions of the driving member 23 and driven member 24corresponding to each of these vane positions. For convenience, each ofthe cylinder vanes 7 has been assigned one of the reference charactersV1, V2, V3, V4 and each of the rotor vanes 6 one of thereference'characters V1, V2, V3, V4. The angle 0, through which arepresentative vane (V1 and V1) from each group turns, is plotted as afunction of time intervals 11, t2, etc., on FIG. 14.

From these it will be seen, that proceeding from the position at t1,shown in FIGS. 4-5, the cam 23 swings through half a revolution withoutaffecting the position of the gear 24. During this time, the cylinder 3is nevertheless being constantly driven, so that its vane V1 advancesfrom the position shown in FIG. 4 to that shown in FIG. 6, while therotor vane V1 remains stationary and thus occupies the same position onboth figures. During this time oil is drawn in through the ports 0 and ainto the chambers formed between vanes V1 and V1, V2 andV2, V3 and V3,V4 and V4, but simultaneously expelled from the chambers between V1 andV2, V2 and V3, V3 and V4, V4 and V1, through the ports b and a.

Next when the cam 23 turns from the position of FIGS. 6 and 7 in thedirection of the arrow into the t3 position shown in FIGS. 8 and 9, oilis drawn into the chambers between vanes V1 and V2, V2 and V3, V3 andV4, V4 and V1, while it is being expelled from between V1 and V1, V2 andV2, V3 and V3, V4 and V4.

* Patented Feb. 1s, was

Further, while the cam23 turns 90 from the t3 position of FIGS. 8 and 9in the direction of the arrow, into the t4 position of FIGS. 10 and 11,oil is drawn into the:

chambers between vanes V1 and V1, V2 and V2, V3 and V3, V4 and V4, whilesimultaneously expelled from those between V1 and V2',.V2 and V3, V3 andV4, V4 and 1.

Finally, when the cam turns another 90 from the t4 7 position of FIGS.10 and 11 to the t position of FIGS.

12 and 13, the chambers between the vanes 1 and V2,

V2 and V3,-V3 and V4, V4 and V1 draw in the oil' connected to outletmeans and the remainder being connected to inlet means, said 'valve'plate ports being posimounted within said casing and carrying aplurality of vanes projecting radially inward from its circumferentialwall, an independently rotatable rotor coaxially mounted I to turnwithin said cylinder and provided with a pluralityof' vanes whichproject radially outward between the vanes carried by the cylinder, atransverse wall closing one end of said cylinder and pierced by a ringof spaced ports, with two'of said ports disposed between each pair ofcylinder-carried vanes, a valve plate forming one end of said casing andpositioned adjacent said transverse wall, resilient means biassing saidtransverse cylinder wall against said valve plate, said valve platebeing likewise provided with a ring of spaced ports, alternate portsbeing tioned to successively register, with said cylinder ports duringeach revolution of said cylinder, means for rotating one of saidcylinder and rotor at a constant first speed, means for driving theother intermittently at twice said speed for half of each cycle, apressure responsive safety valve mounted in said valve. plate, those ofsaid valve plate ports con'n'ectedtdan outlet beingalso connected to oneside of said pressure responsive safety valve and those connected to aninlet being also connected tothe other side of said safety valve, sothat an excessive outlet pressure is relieved by passage of fluid fromsaid outlet connected ports to said inlet connected ports through saidsafety valve, and means accessable from outside said casing foradjusting the loading of said pressure respon sive valve.

- References Cited by the Examiner.

UNITED STATES PATENTS 2,211,292 8/40 Ryerson 123--11 2,833,225 5/58,Sherman 103--161 X 2,948,221 8/60 Carver 103-203 x 3,023,706 3/62 DeFezzy at al. 103-26 X FOREIGN PATENTS 758,187 10/56 Great Britain.

34,035 12/12 Sweden.

JOSEPH H. BRANSON, IR., Primary Examiner.

LAURENCE V. EFNER, Examiner.

